Hydraulic power lift mechanism



Feb. 22, 1949. 'W. H. WIORTHINGTON z'rm. 7 2,462,246

HYDRAULIC POWER LIFT uacmmrsu Filed Au 4, 1944 s Sheets-Sheet 1 INVENTORS WAYNE H. WORTHINGTON MIL F. JIRSA ATTORNEYS Feb. 22, 1949; w. WORTHINGTON ETAL 6 Sheets-Shget 2 Filed Aug. 4, 1944 m QE IN VENTORS WYNE H. WORTHINGTON ATTORNEYS Feb.2 2, 1949. w. H. WORTHINGTON ETAL 2,452,246

HYDRAULIC POWER LIFT MECHANISM v Filed Aug. 4, 1944 6 Sheets-Sheet 3 2f LL IN V EN TORS Feb; 22, 1949. w. H. WORTHINGTON EI'AL ,4 I

HYDRAULIC POWER LIFT MECHANISM Filed Aug. 4, 1944 r 6 sheets sheet 4 I88 79 I88 INVENTORS 235 2 2 9 WAYNE H. WORTHINGTON m g 2\ F. JIRSA |4Q I78 I77 76 1 Feb. 22, 1949. w. H. WORTHINGTON EIAL 2,462,245

HYDRAULIC PowEn LIFT macmmzsm Filed Aug. 4, 1944 6 Sheets-Sheet 5 INVENTORS WAYNE H. WORTHINGTON IL F. JIRSA ATTORNEYS FIG. 8

Feb. 22, 1949. w. H. WORTHINGTON E A; 2,462,246 I I HYDRAULIC POWER LIFT MECHANISM Filed Aug. 4, 1944 6 Sheets-Sheet 6 269 270 269 270 '298 FIG. ll LLJJ 245 LLJJ 2w 280 r 28 WAYNE H 'lfifiwow l 247 248 IL EJIRSA FIG. I2 287 288 Patented Feb. 22, 1949 HYDRAULIC POWER LIFT IHECHANISM Wayne H. Worthington and Emil F. Jirsa, Water-' loo, Iowa, assignors to Deere Manufacturing (30., a corporation of Iowa Application August 4, 1944, Serial No; 548,086

The present invention relates generally to bydraulic mechanism and more particularly to hydraulic power lift mechanism adapted for use on farm tractors and the like, and is in the nature of an improvement over the hydraulic mechanism shown and described in an application, Serial No. 453,907, filed August 6, 1942, by W. H. Worthington, now Patent 2,403,422, granted July 2, 1946.

The principal object of the present invention relates to the provision of a novel and improved hydraulic mechanism for independently controlling a pair of oppositely extending, coaxially disposed rockshafts, whereby a pair of implements mounted on opposite sides of .the tractor, such as, for example, a two-row cultivator, may be independently raised and lowered, so that when cultivating crop rows that terminate along a line disposed at an acute angle to the rows, each cultivator can be independently raised when the latter reaches the end of the row. Conversely, the individual cultivators can be lowered at the beginning of the rows in cases where the rows on opposite sides of the. tractor do not begin at the same point in the path of the tractor.

Another object of our invention relates to the provision of a hydraulic control mechanism which is provided with a pair of oppositely extending rockshafts built into the casing of the mechanism and having independent hydraulic cylinders for actuating the rockshafts, the cylinders being built in as an integral part of the mechanism, with the further provision of means for converting the control mechanism for controlling a pair of remotely positioned hydraulic cylinders when desired, and with the still further provision for converting the control mechanism for controlling a double acting hydraulic cylinder in which fluid can be applied under pressure to either end of the cylinder. A more specific object relates to the provision of an auxiliary device in the form of a valve case attachment which can be connected to the main control mechanism so that the latter can be used to control one double acting cylinder instead of two single acting cylinders.

Another more particular object relates to the provision of a novel and improved hydraulic cy1- inder assembly consisting of a unitary casting which contains two cylinders and the supply ducts therefor, of a shape and size which permits installing between the two drive gears on the rear axles of a tractor, within the usual banjo typ axle housing. In this assembly, the two cylinders are provided with connections to the rockshafts which are so constructed and arranged 7 Claims. (CI. 60-97) 2 that although the two cylinders are of different diameters and different distances from the rockshafts, the two rockshafts are moved by the hy-' draulic mechanism through the same angular range and with the same lifting capacity.

Still another object relates to the provision of a novel and improved hydraulic mechanism which incorporates a dual hydraulic pump having a separate pair of pump gears for each of the two cylinders, thus providing for moving the two rockshafts at the same rate of speed, regardless of whether therockshafts are moved simultaneously or independently. When a single hydraulic pump is used for controlling a plurality of cylinders, assuming the pump to be of the constant displacement type as is usual in this type of mechanism, the cylinders work at a faster rate of speed when one cylinder is operated independently than when more than one cylinder is operated at a time. An even more specific object of the invention relates to the provision of a novel and improved dual discharge pump which is especially compact and simple and is inexpensive to manufacture but is efllcient and durable in operation.

A further object of our invention relates to the provision of a novel and improved check valve which can be manually opened against pressure with a minimum of efiort.

These and other objects and advantages of our invention will be apparent to those skilled in the art after a consideration of the following description,- in which reference is had to the drawings appended hereto, in which Figure l is a rear elevational view of the rear axle housing of a tractor equipped with hydraulic mechanism embodying the principles of the presv ent invention, the axle housing and power lift casing being broken away to show the hydraulic cylinders, rockshafts, and connections therebetween.

Figure 2 is a sectional elevational view taken through the pump casing along a line 2-2 in Figure 1.

Figure 3 is a rear elevational view of the axle housing and hydraulic mechanism, casing, showing the pump partially disassembled, that is, with the end plate removed, as indicated by a line 33 in Figure 2.

Figure 4 is a rear elevational view of the pump casing with the rear end plate and also the rear pump unit removed, as indicated by a line 4-4.

in Figure 2.

Figure 5 is a side elevational view of the axle through the alineIIinFigure6,

Figure 8 is a sectional elevatlonal view taken valve casing along a line H in Figure 6.

Figure 9 is a similarsectional elevational view '-takenalongallnel-'-3inFigure6.

'Figure 10 is a rear elevational view taken through the auxiliary valve casing along a line 7 l3|3inFlgure8. a

Figure 11 is a sectional plan view taken alon alinell-IlinFigurelO.

Figure 12 is a sectional plan view taken along aline l2--|2inFlgure l0. 1

Referring now to the drawings. the rear axle housing of the tractor is of a conventional banjo type and is indicated in its entirety by reference numeral l5, and comprises a centrally disposed enlarged gear chamber lianda pair of laterally oppositely extending axle housings or quills 11, within which are disposed apair of conventional drive axles II. The inner ends of the two axles l8 terminate inlaterally spaced relation and each of the axles I8 is provided with alarge drive gear I; the two gears llbeing rigidly'flxed adjacent the inner ends of the axles I8 and secured to the latter by nuts 20. The drive gears I! are spaced apart laterally and mesh with driving .gears (not shown) disposed within a tractor transmission housing 2| (Figure 5) ahead of the axle housing l5, the driving gears being suitably connected to a tractor engine through differential gear mechanism, none of which forms any part of the present invention and is therefore not shown herein, 9.!- though the details of a transmission of this type are found in Patent 2,103,543, granted to McCormick and Worthington, December 28, 1937. The central gear chamber lBis providedwith a large .opening 22 in the .rearside thereof to provide access to the gears l9 and nuts and this opening 22 is sometimes covered by a cover plate that is dished out rearwardly to. accommodate the gears [9 which extend rearwardly through the opening-22; as shown in the above-mentioned patent. According to the present invention, however, the opening 22 is covered by a power lift casing 23in the form of a casting having a peripherally extending flange 24 which fits over the 7 housing opening 22 and is secured to the latter by a series of cap screws.25.

The upper portion of the casing 23 is provided with a pair of laterally oppositely extending tubular arms 30, within which are journaled a pair of power lift .rockshafts 3|, which are coaxially disposed with their inner ends spaced closely together and their outer ends extending outwardly through the ends of the tubular arms'30. The

rockshafts 3| are cylindrical throughout except for the inner and outer ends 32, 33 which are .of substantially square cross section, the outer ends 33 being adapted to carry suitable lifting.

arms (not shown), to which implements associated with the tractor can be connected for transmitting lifting force thereto. A pair of bearing hubs 34 are cast integral with the casing 23 in laterally spaced relation and support the inner ends of the rockshafts 3| for rocking movement within the arms 30. The outer ends of the rockshafts 3| are journaled in a pair of closure bushlugs 35, which are provided with mounting flanges 4 I 33. the latter being secured to the ends of the tubular arms 33 by suitable cap screws 31 (Figure 3) The rockshafts 3| arerocked about their common axis, by meansof a pair of actuating arms 43, 4|, respectively, which are supported on hubs 42, 43, which are tightly clamped on the inner squared ends 32 of the rockshafts 3| by means of cap screws 44. 'Thearms 40, 4| extend downwardly from the inner ends of the rockshafts in a side-by-side-relation, the lower ends of the arms beingswingably connected by pins 45 to a pair of piston rods 4', 41, respectively. The'latter extend forwardlythro'ugh the rear openin 22 in the axle gearchamber l8 and areswinzably connected at their forward ends to pistons 43, 4! by suitable wrist pins 50. The two pistons 43. 43 are slidably disposed within a pair of horizontally positioned cylinders 5|, 52, formed in a umtary cylinder casting 53, which lies between the two drive gears i9 within the chamber l6 and above the axles IS. The cylinder casting 53 is provided at its rear end with a supporting flange 54, which is rigidly mounted by means of suitable cap screws 55 on the front wall of the power lift casing 23. The rear ends of the cylinders 5|, 52 are open and register with'ah opening 51 in the front wall 56, through which aligned openings the piston rods 46, 41 extend. r

Inasmuch as the lateral space between the gears I9 and also the vertical space between the nuts 20 and the top of the banjo housing I5 is of extremely limited dimensions, it was necessary to design the cylinder casting 53 in a unique form in order to accommodate two lifting cylinders of sufllcient capacity to provide the desired lifting torque at the rockshafts 3|. Thus, by virtue of the narrow space between the gears IS, the two cylinders 5|, 52 are spaced vertically from each other with the result that the lower cylinder 52 is obviously a greater distance from the axis of the rockshafts 3| than is the upper cylinder 5|.

Therefore, one of the actuating arms 4|, for the lower piston rod 41, is appreciably longer than the other actuating arm 40 which is connected to the upper piston rod 46. It is desirable, however, to provide a lifting hydraulic mechanism which applies an equal torque at the two rockshafts 3|, for most tractor mounted implements adapted for mounting on the two sides of the tractor are substantially equal in weight. Furthermore, it is desirable that both rockshafts 3| be rocked at the same rate of speed in order to make the time required for lifting the implements substantially equal. To accomplish these purposes, thelower cylinder 52 was made of a smaller diameter than the upper cylinder 5| so that the area of the working face of the piston 49mu1tiplied by the length of the moment arm of the actuating arm 4| is equal to the area of the working face of the upper piston 48 multiplied by the length of the shorter actuatin arm 40. Thus, assuming equal pressures applied to the working faces of the pistons, equal torques are applied'to the rockshafts 3| embodiment, we have made the lengths of the actuating arms 48, ll, equal respectively to the lengths of stroke of the corresponding pistons. The strokes of the two pistons are definitely limited by means of stops which will be described later.

The cylinder casting 53 also incorporates a pair of supply ducts 68, 6|, which are cored into the walls of the casting and extend along the cylinders substantially parallel thereto to the forward ends thereof and communicate with the cylinders through suitable ports 62, 63 at the forward ends. As best shown in Figure l, the supply passage 88 forthe upper cylinder 5| occupies the space beneath the latter cylinder and alongside of the lower cylinder 52. This space is provided by offsetting the lower cylinder 52 to one side of the center line of the upper cylinder 5 I, which is made possible by the smaller diameter of the cylinder 52. The supply passage SI for the lower cylinder 52 is disposed beneath the latter and just above the axle nuts 28.

The hydraulic fluid, preferably oil, is supplied to the cylinders under pressure by means of a pump I8 of the constant displacement typ which is mounted on the rear wall II of the power lift casing 23. A reservoir 12 is pro'fided between the front and rear walls 56, II and the bottom of the reservoir is defined by a bottom wall 13 (see Figure 5). The pump I8 comprises two pairs of intermeshing driving and driven gears 15, I6, and I1, 18. Each pair of intermeshing gears constitutes a separate and independent pumping unit for supplying fiuidto the two cylinders 5|, 52, respectively. Hence, each of the two pairs of intermeshing gears is enclosed within its own separate compartment in a pump housing which comprises a series of laminations or plates, including a front or inner housing plate I I which is actually a por tion of the rear wall II of the power life casing 23 and has a machined rear surface 19 against which the adjacent housing plate 88 is secured. The plate 88 is annular in form, the inner portion being cut away to provide a pair of intersecting cylindrical openings 8|, 82 within which are rotatably disposed the two pump gears I1, 18, respectively. The cylindrical openings 8|, 82 are the ends of the gear teeth and along the sides of the gears.

The two drive gears, I5, 1! are mounted on a power take-off shaft 93, which extends rearwardly from a suitable connection (not shown) with the.

' rearwardly, through the end plate 89 and is Jourreservoir 12, from which the oil is trapped bemade of a diameter suitable for receiving the ends of the gear teeth 83 which are slidable therein, but fit closely in order to maintain a fiuid pressure therebetween, as is well-known to those skilled plate 88 is equal to the thickness of the gears 11,

I8 plus a slidin clearance, so that pressure is maintained within the pump compartment. The partition plate 85 also serves as the forward wall of the second pump compartment which is formed by a pair of intersecting cylindrical openings86, 8! disposed within a second housing plate 88, which lies tightly against the rear face of the partition plate 85. The rear wall of the second pump compartment comprises an end plate 89, and the plates 88, 85, 88,. and 89 are securely clamped together and to the rear wall 'II' of the power lift casing 23 by means of suitable cap screws 98. The intermeshing gears I5, 16 are rotatable between the partition plate 85 and the end plate 89, with sliding clearance to permit rotation of the gears but preventing leakageof oil around naled in a bearing 96 mounted on the rearward side of the end plate 98. The rear end of the power take-off shaft behind the bearing 98 is provided with splines 91, adapted to receive a power connection for implements associated with the tractor, as is well-known to those skilled in the art. Each of the drive gears I5, 1! is apertured to receive the power take-01f shaft 93 and is suitably keyed thereon, and the partition plate is provided with an aperture 98 through which the shaft 93 extends. The driven gears I6, I8 are mounted on a stub shaft 99, which is journaled at opposite ends thereof, respectively, in a pair of sockets I88, i8I (see Figures 5 and 1), preferably integrally cast within the plates II and 89, respectively.

Oil is drawn into the pump through an intake opening I85 in the rear wall II. of the casing 23 and through an axially aligned opening I88 in the partition plate85. Thus, the two pairs of gears have a common intake passage from the tween the teeth of the gears during rotation of the latter and carried around the gears within the spaces between the teeth and discharged at the sides of the gears opposite the intake opening, by virtue of the meshing of the teeth which prevents the oil from carrying back to the intake, as is well-known to those skilled in the art. The oil from the forward pair of intermeshing gears I8, I8 is discharged from the compartment through an opening I I8 in the casing wall I I which communicates with a high pressure duct III cast integrally with the power lift casing. The oil discharged from the rear pair of gears I5, I8 is directed through a groove I I2 formed within araised portion I I3 in the end plate 89, which groove communicates with an axially extending opening H4 in the annular plate 88, the latter being disposed in axial alignment with a similar opening H5 in the partition plate 85, an aperture H6 in the annular plate 88, and a port III in the casing wall II. The port III communicates with a high pressure duct II8, cast integrally with the casing wall and offset around the other high pressure duct III, as best shown in Figure 2. Thus, it is evident that each of the pairs of intermeshing gears operates as an independent pumping unit which can develop pressure independently of the other, although the rates of delivery of oil from the two pumping units are equal, since the pumping units are of the constant deliverytype. As will be understood later, the discharge from one of the pairs of gears I5, 16 serves the upp r cylinder 5I through the high pressure supply duct III while the other pair of gears 11, I8 supplies the other cylinder 52 through the duct II 8. The control of the two cylinders is accomplished through a dual control mechanism contained within a control casing I28 which is mounted on the rear side of the power life casing 23 by means of cap screws I2I, which extend through suitable apertures I22 (see Figure 6) in the control casing rear side of the casing 23. The front side of the valve or control casing I28 is provided with a large opening I25 (Figure 6), which registers with a large opening I26 in the rear side of the power a lift casing 23 so that the two casings are disposed in communication with each other for purposes which will appear later.

The two high pressuresupply passages I I I, II8 extend upwardly within the power lift housing 23 and have ports I30, I3I (Figure 3) which are disposed in register with a pair of laterally spaced ports I32, I33 in the control casing I20, respectively. The two ports I32, I33 communicate with a pair of independent valve mechanisms I34, I35, respectively, which include ducts and passages cored or drilled in portions I36, I31 of the cast housing I20 on opposite sides thereof, respectively, as best shown in Figure 6, with shiftable valve members within the passages, as will be described in detail. However, since both valve mechanisms I34, I35 are substantially identical, only one of the mechanisms I34 will be described in detail.

Referring now more particularly to Figures 6 to 9, inclusive, the port I32 in the casing I20 communicates with a supply duct I40 which extends upwardly from the port I32, turns rearwardly at HI and then has a second vertical portion I42 extending upwardly from the rearwardly extending portion I4I. Adjacent the upper end of the vertical portion I42 are a pair of rearwardly facing ports I43, I44, which communicate with a vertical valve passage I45, the upper end of which terminates in a port I46 which opens to the hollow interior I41 of the valve casing I20. Within the vertical valve passage I45 is disposed a vertically slidable valve member I48 comprising an upper stem portion I48 of reduced diameter and a pair of vertically spaced closure portions or pistons I50, II connected by a lower stem portion I52 of reduced diameter. In Figure 8, the valve member I48 is disposed in a neutral position in which the piston or closure portion I50 is disposed below the port I43, permitting the supply of oil from the pump to flow through the port I43 and upwardly through the exhaust port I46, into the interior I41 of the casing I20, from which the oil flows outwardly through the opening I25 in the front wall of the casing I20, and into the reservoir 12 through the opening I26 in the rear wall of the power lift casing 23. Hence, in this position of the valve member I48, the oil from the pump merely circulates at substantially no pressure.

The valve member I48 can be shifted upwardly until the piston portion I50 blocks the exhaust port I46 and at the same time uncovers the lower port I44 in the supply duct I42, thereby permitting oil to flow downwardly through the valve passage I45 to the upper port I55 of a U-shaped by-pass duct I56 which extends downwardly through the casting and has a lower port I51 communicating with the lower end of the vertical passage I45. When the valve member I 48 is raised to a position blocking the exhaust port I46, the valve passage I45 is blocked by the lower piston I5I just below the port I55, 50 that the oil flows downwardly from the port I44 along the stem I52 and into the U-shaped by-pass duct I56, which communicates through the port I51 with a valve port I58. The valve port I58 is normally closed by a check valve I59 of the poppet type, which is urged upwardly by means of aspring I60 into seating relation in the port I50.

- The poppet valve I50 wardly extending hollow stem I6I, which is slidis provided with an upably mounted within a bushing I32, the latter being tightly disposed within the valve passage I45, forming a closure for the latter and thereby closing off the valve passage I45 between the upper portion and the check valve seat III at the lower end, although the upper and lower portions are permanently interconnected by the bypass duct I56. The interior of the hollow stem I6I of the check valve communicates with a valve seat I63 in the head of the poppet valve I53. A small poppet valve I64 is normally held in seating relation in the seat I33 by means of the coil spring I60, which bears against the head of the valve I64 and reacts against a plug I65 which is threaded into the lower endof a chamber I66 dis- .posed coaxially with the valve passage I45 but slightly larger in diameter. Thus, the spring I60 acting against the head of the valve I64 not only holds the latter valve against its seat I63 but also holds the check valve I58 against its seat in the end of the valve port I58 by a force transmitted through the inner seat I63. The inner valve I64 is provided with a stem I61 which is slidably disposed within the hollow stem I6I and extends upwardly beyond the end of the latter, in a position to be engaged by the lower end of the valve member I48.

The control mechanism disclosed herein is adapted to be used for controlling three different arrangements of hydraulic motors. First, each of the valve mechanisms I34, I35 can be used to control its respective integrally mounted cylinder 51, 52 for actuating the two coaxial rockshafts 3|, respectively; second, each of the valve mechanisms I34, I35 is adapted to be used to control a supply of oil under pressure to an independent remotely positioned hydraulic motor (not shown); and third, the two valve mechanisms I34, I35 can be used in conjunction to control the flow of oil to the opposite ends of a double acting hydraulic motor indicated in Figure 11 by reference numeral I10, and which is positioned remotely from the valve mechanism but connected thereto by suitable flexible hoses I1I, I12.

The chamber I66 is connected in communication with the integral cylinder 5I as follows: A cored passage I15 extends forwardly and inwardly from the chamber I66 and communicate with a forwardly extendingpassage I16 within which is tightly fixed a bushing I11 (see Fig ures 7 and 9). The bushing I11 is provided with a central passage I18, the rear end of which is provided with a valve seat I19 and the forward end of which is disposed in register with a cored passage I80 within the power lift casing 23 (see Figure 5). The passage I80 extends forwardly and curves upwardly through the casing 23 and g has a forward end which is disposed in register with the rear end of the cylinder duct 60 which is connected through the port 62 with the front end of the upper cylinder 5I. Similarly, the other bushing I11 in the valve mechanism I35 has an interior passage I18 which communicates with the cylinder duct 6I through a second cored passage I8I curving downwardly and extending forwardly through the casing 23.

Hence, when the valve member I48 is raised to block oil the exhaust port I46 and connects the port I44 with the by-pass I56, the oil from the high pressure duct I42 flows downwardly through the by-pass I56, forcing the check valve I59 downwardly away from the end of the port I56, whereupon the oil flows from the chamber I66 through the passage I15, the bushing passage I18, the cored passage I80, the cylinder duct 80, and into the upper cylinder I through the cylinder port 82, thereby forcing the piston 48 rearwardly within the cylinder 5| and acting through the piston rod 48 and arm 40 to rock the rockshaft 8I on the left side of the tractor.

The piston 48 can be stopped at any point within its range of stroke by merely shifting the valve member I48 back to a, neutral position as shown in Figure -8, whereupon the oil from the pump is again exhausted through the port I46, while the oil within the cylinder 5| is locked therein by the check valves :59 and I84. However, should the valve member I48 be left in its working position in which 011 is being supplied to the cylinder 5|, the latter will travel over its entire stroke until the arm 40 engages a stop I85, cast integrally with the valve casing I (Figures 6 and 9). This stops the rearward movement of the piston in its lifting stroke, which immediately results in a rise in pressure within the supply duct. This pressure is relieved through a relief port I86in the portion I4I of the passage I40, which port is normally blocked by a poppet valve I81. held closed by a strong compression spring I88 dis posed within a passage I89 in the casing I20. The passage I89 is disposed vertically and is closed at the bottom by means of a plug I90 threaded into the end of the passage I89. The plug I90 serves to take the reaction of the spring I88 to hold the valve closed. The valve I81 is provided with an upwardly extending stem I 9i within a socket I92 and the stem I9I is provided with an axially extending opening I93 therethrough. An increase in pressure in the duct I forces the valve I81 downwardly away from the relief port I88 against the pressure of the spring I88, permitting the oil to fiow through the-port I86 into the passage I89 and from there upwardly through the hollow stem I9I into the upper end of the socket I92, which is extended beyond the end oi the stem I9I. The upper end of the socket I82 is connected by a transverse passage I 94 with a fore and aft extending passage I95 in the side. wall of the casing I 20, extending rearwardly to a second transverse passage I96 connected to a vertically disposed valve passage I91. A valve member I98 is slidably disposed within the passage I91 and comprises an upper actuating stem I99, a. cylindrical portion having a groove 200 extending circumferentially thereof and a pair of vertically spaced piston or closure members MI, 202 interconnected by a neck 208 of reduced diameter. A detent ball 204 engages the groove 200 and is disposed within a transverse passage 205 (Figure 9), within which is disposed a compress on spring 206 serving to urge the detent ball 204 into the groove 200, and thereby to hold the valve member I 98 in closed position, as indicated in Figure 8. In this position of the valve member I98, the closure member 20I blocks the passage I91, thereby preventing oil from flowing from the valve passage I through a short interconnecting passage 209 and upwardly through the passage I91 to the interior l41 of the casing I 20. However, when the rockshaft arm 40 engages the stop I 85, causing the pressure to rise in the supply duct and open the valve I81 against the spring I88, the oil flows therethrough and through the hollow stem HI and passages 1o valve neck 208 to hold the valve in raised posi tion. In this position the closure portion "I is above the opening into the interior I41 of the casing, thereby permitting the oil to flow outwardly and return to the reservoir, thereby relieving the pressure in the supply duct and allowing the spring I88 to close the valve I81. The check valves I59, I64 a e closed by the spring I to hold the oil locked in the cylinder and thereby lock the piston 48 at the end of its raising stroke.

To return the piston to the forward end of the cylinder, the main valve member I48. is shifted downwardly beyond the neutral position shown in Figure 8, whereupon the the lower end of the valve member I48 engages the upper end of the inner valvestem I61, thereby forcing the inner valve I64 open, permitting oil to flow from the cylinder 5I upwardly through the inner seat I63 in the valve I59 and through a plurality of radially extending holes 2I0 in the tubular stern I6I, and through the port I51 upwardly through the by-pass I58 into the valve passage I45.

Since the piston I50 blocks the upper end oi the passage I45, the oil flows downwardly along the neck I52 into a chamber 2I I. The chamber 2 is connected by a. transverse passage 2I2 (see Figure '1), with a valve port 2I8 which exhausts the oil to the interior I41 of the casing I20.

Moving the valve member I48 still further downwardly, causes the end of the valve member to engage the upper end of the tubular stem I6I of the valve I59, thereby opening the latter valve and permitting the oil to flow under the main poppet valve I59. The purpose of the two con-= centric valves I59, I84 is to avoid the necessity for applying a heavy pressure downwardly upon the valve member I48 to force a large diameter valve open against the pressure in the cylinder 5I, which is comparatively high when there is a heavy load supported on the rockshaft 3|. By providing a small diameter valve I64, which is opened in advance of the main valve I59, a much lower pressure against the valve member I48 is required to relieve the pressure in the cylinder, after which the main valve I59 can be opened with comparative ease.

The valve member I48 is provided with a head 2 I5 which has a laterally extending arm 2I8 engageable with the upper stem I99 on the exhaust valve member I98, to reset the latter when the main valve I48 is moved downwardly to open the check valve I64, I59. This returns the exhaust valve member I98 to its neutral position with the detent-ball 204 in engagement with the groove 200, as shown in Figure 8.

A valve 2I1 is provided (see Figures '7 and 9),

- positioned in the exhaust port 2I3 to restrict the I94, I95, I98, into the. lower 'end of the valve passage I91, acting against the lower end of the closure portion 202 to force the valve member I98 upwardly until'the ball detent 204 engages the flow of oil from the cylinder 5| back through the port 2I3 into the interior I41 of the casing I20 and thus back to the reservoir 12. This valve 2 I 1 is supported on a threaded shaft 2I8, which ex tends outwardly through the rear wall of the easing I20 through a threaded opening 220. the outer end of the threaded end 2 I8 being providedwith a notch 22! adapted to receive a screw driver, for the purpose of adjusting the valve 2I1 inwardly or outwardly with respect to the exhaust port 2I3 to regulate the rate of flow of oil back to the reservoir. By this adjustment, the rate of return of the piston to the forward end of the cylinder 5| can be adjusted for the purpose of adjusting the speed of lowering of the load connected to the rockshaft 8|. The valve 2" can the seats I" in the ame be secured in adjusted osition by means of a lock nut 222 which engages the threaded stem 2I3 outside of the casing I20 and this adjustment is further protectedby means of a threaded cap 223 which can be screwed onto the end or tile threaded stem 2I5.

A coil spring 345 encircles the rockshaft 3i and I has one end 345 bent into a U-shape to engage a pin 341 in the rockshaft 3I. The other end of the coil spring 345 is turned in a direction parallel to the axis of the rockshaft, as indicated at 345 and engages a socket 343 in the inner end to return the rockshaft 3| to its normal or lowered position in the event that the load connected to the rockshaft is insufficient to move the pis- I n auxiliary valve casing 245 is mounted on the rearton forwardly when the valve mechanism is set to exhaust the cylinder Obviously. the return movementof the pisto 45 toward the forward end of the cylinder i can be interrupted at any time within its stroke by returning the valve member I43 to the'neutralposition 'as shown in Figures, whereupon the spring I50 closes the check valves I50, I54 immediately, thereby locking any remaining oil within the cylinder 5I and stopping the piston 45. A mechanism for automatically actuating the valve member I45 to neutral position at any predetermined point in the range of movement of the piston 45 will be described later.

Access may be had tothe two valve members I45, I55 on each side of the casing I25 through a pair of openings 225 in the top wall 226 of th casing I20 at opposite sides thereof, respectively. the openings 225 being covered by cover plates 221 secured to the casing by a pair of cap screws 225 engaging the top wall 225 on opposite sides of the opening 225, respectively.

An opening 235 extends rearwardlv from the chamber I55 through the rear wall of the casing I20, the rear portion of the opening 230 being threaded as indicated at 23I. The opening 23I is blocked by a plug 232 when the valve mechanism is being used to control the inte ral cylinders 5I. 52 and also whenthe double acting cylinder I is connected for operation. When it is d sired to operate a pair of sing e. act ng remote cylinders, however, the plugs 232 are removed and are replaced by hose connecting fittin s 233 which are threaded'to permittheir nstal a in the threaded o enings 23!. Flex ble been 73 are attached to the hose fittings 233 and serve 'to conduct fluid under pressure from the chambers 7 I55 beneath the check valves 155,154 to suitable single acting remote cylinders (not shown). when the remote cylinders are connected, it is desirable to render inoperative the'integral cylinders 5I."52and this is accomplished by means' oij-va'ives. 235 (seeFigures 7 and 9), adapted to rear ends of the bushings I11. Each valve 235 is supported on a threaded stem Y 235, which extends through a bushing 231,'which screws into a threaded opening235 in the rear wallof the casing I25 in register with the passage I15. The interior of the bushing 231 is threaded to receive the threaded stem 235, permitting the latterto be adjusted inwardly or outwardly relative to the bushing 231, to'move the valve 235 into and but of blocking engagement in the seat I19. The outer end of the stem 235 is provided with a notch 235 adapted 12 to'receive a screw driver for adjusting the valve 235. When the remote cylinders are connected to the casing I20 by the fittings 233, the valves 235 should be closed by screwing the stems 233 g inwardly, but when the equipment is converted for operation of the rockshafts 3i, this valve 235 is backed away from the seats I to permit the .oil to flow freely through the passage I15, in which case the threaded openings 23I are closed 10 by the plugs 232, as indicated in Figures 3, 5 and 8. Lock nuts 240 are provided to lock the valve stems 235 in adjusted position and the stems are also protected by threaded caps 24I which screw on the ends of the stems 235. 15 When the control equipment is to be used in connection with a single double acting cylinder I15, both shut-off valves 235 are closed and both of the remote cylinder hose connections 233 are replaced by plugs 232.- For this operation, an

. side of the control casing I25 and secured thereto by suitable cap screws 245. The auxiliary casing 245 is a casting in which are disposed a pair of laterallyspaced vertically extending valve pasu sages 241, 245,, the lower ends of which are closed -'by plugs 245.andthe upper ends being enlarged to form chambers 250, 25I,respectively. Each of the vertical valve passages is provided with a shiitable valve member 252 comprising a poppet valve 253 adapted to block the upper end of the 1 passage 241 or 245 and being normally urged into 4 closed position by a compression spring 254 disposed within thechamber 250 or 25I. .The upper ends of the springs 254 bear against a pair of plugs 255 which are threaded into the upper ends of the chambers 255, 25l, respectively. Each of the valve members 252 further includes a neck portion 255 of reduced diameter extending downwardly from the poppet valve 253 and carrying on its lower end a piston or closure portion 251. The

lower end of each of the valve passages 241, 245

communicates with the respective auxiliary valve passage I51 in the valve casing I through a pair of fore and aft extending registering ducts 255,

259 disposed in the adjacent walls of the auxiliary casing 245- and control casing I20, respectively.

The upper end of cache! the valve passages 241 is connected with the interior I 41 of the casing I20 by a short forwardly extending passage 250,

Which registers in alignment with an opening I in theback wall of the casing I 20.

A .pair of coaxially disposed transverse ducts 252, 253 are drilled inwardly from the opposite sides of the casing 245,1niersecting the chambers 250 and 25], respectively. The outer ends of the ducts 252, 253 are closed by plugs 264 while the inner ends of the ducts intersect a pair of fore and aft extending passages 255, 255, within which are slidably disposed a pair of valves in the shape of thimbles 251. The thimble valves 251 are slidable from the open position shown in Figure 11 rearwardly to, aclosed position blocking the ducts 252, 253 and are urged toward closed position by a pair ofcompression springs 253, respectively.

The springs 255 bear against the inside of the heads oi the valves 251-and against the outer wall of the valve casing I20, which fits tightly against the auxiliary casing 245 to prevent leakage of oil from the openings 255, 255. In their closed position, the valves 251 areurged by the springs 253 into engagement with shoulders 255 on the opposite side of the ducts 252; 253. The

rear ends of the passages 255, 255 are smaller in diameter and are threaded as at 210 to receive 13 Y connected by suitable hose connection fittings 212. The inner, ends of the bushings 2" are provided with a pair oi legs 213, which engage the heads cylinder I18, no attention need be given the thimble valves 281, for they are automatically opened by screwing in the bushings 2". Likewise, when the mechanism is to be converted to operation of the integral cylinders or the single acting remote cylinders, the bushings 21I are removed whereupon the springs 288 close the valves 281. When the double acting cylinder I18 is not connected for operation, the-bushings 2" are replaced by plugs 215, which prevent dirt from entering the threaded openings 218 and also guard against leakage of the oil outwardly past the valves 281. If desired, the auxiliary valve casing 245 can be removed entirely and the openings 258, 28I in the rear wall of the casing I28 can be plugged by any suitable means such as by threaded plugs (not shown).

In the normal position of the valve members 252, in which the poppet valves 253 are held closed 14 through the connecting hose I12 to one end of the double acting cylinder I18. The cylinder I18 by the springs 254, the valve pistons 281 at the of check valve ports 282, 283, within which are seated a pair of check valve 284, 285, respectively. The check valves are provided with stems 288, which are slidably disposed within sockets 281 which extend rearwardly into a bulge 288 in the auxiliary casing 245. The check valves are urged toward closed position by a pair of coil springs 288 which bear against the rear wall of the control casing I28. moved against the compression of the springs 288 into a pair of valve chambers 288, 28I in the form of recesses in the front wall of the auxiliary casing 245, which is tightly secured against the rear wall of. the casing I28. The valve chamber 288 on the left side of the casing 245 is connected by an upwardly inclined cored passage285 with the inner end of the upper'transverse duct 283, which extends inwardly beyond the passage 286. Likewise, the valve chamber 28I on the right side of the casing 245 is connected by an upwardly inclined passage 286 with the inner end of the upper transverse duct 262, extended inwardly beyond the passage 261. The two inclined passages 285, 288 are thus disposed in crossed relation to each other but do not intersect, for the passage 288 is offset at 281.

When pressure is applied from the high pres- The check valves 284, 285 can be sure supply duct through the connecting ducts 258, 258 into the lower end of the vertical valve passage 241 on the left side of the casing, the pressure acts against the lower end of the valve piston 251 forcing the latter upwardly against the spring 254 until the transversepassage 288 is uncovered by the piston 251, permitting the oil to flow laterally inwardly, through the check valve port 282, forcing the valve 284 open against the action of the spring 288 into the valve chamber 288. The oil continues upwardly through the passage 285 into the duct 283, and since the poppet valve 253 in the valve passage 248 is held closed by the spring 254, the oil flows outwardly through the bushing in the opening 288 and is provided with a piston 2.81 slidable therein, connected to a piston rod 288 which extends outwardly through a sealing gland 288 in the end of the cylinder and has a connecting eye 888 fixed to the outer end of the rod 288 for bolting the latter :to a load which is desired to be moved by the piston. The oil flowing into the cylinder through the hose I12 forces the piston 281 downwardly as viewed in Figure 11, thereby forcing oil from the other side of the piston outwardly from the cylinder through the other hose [1i and in through the bushing 2" to the passage .285 and duct 262. The oil cannotfiow downwardly through the passage288, for the check valve 285 is closed and the piston valve 251 also closes the duct 28I and therefore the oil flows outwardly through the duct 282 into the chamber 258, and since the valve member 252 is raised by the pressure of the oil under the piston 251, the oil is free to flow downwardly into the passage 241 and out into the reservoir through the exhaust duct 288 which is aligned with the opening 28I.

When the pressure is relieved from the inlet duct 258, the spring 254 closes the valve 258 and returns the piston 251 at the lower end of the stem 258 into closed position, cutting ofi the flow of oil through the duct 288, whereupon the piston 281 in the double acting cylinder I18 immediately stops moving.

The piston 281 can be moved in the opposite direction within the double acting cylinder I18 by applying pressure to the lower end of the valve passage 248 on the right side of the casing 245,

forcing the valve piston 251 upwardly, uncovering the duct 28I, whereupon the oil flows therethrough, forcing open the check valve 285 and flowing upwardly through the chamber 28I and passage 286 into the duct 282 and since the valve 258 is closed blocking the upper end of the valve passage 241, the oil flows out through the bushing 21I in the passage 265, through the hose I" to the lower end of the cylinder I18. Upward movement of the piston 281 forces oil outwardly through the hose I12 into the casing 245 through the bushing 2H, and since the oil cannot flow downwardly through the passage 285 as the latter is blocked by the check valve 284, the oil flows into the upper end of the valve passage 248, under the poppet valve 253 which is held open by the pressure under the piston 251, and flows through the exhaust duct 268 back to the reservoir.

It will be noted that when the double actin cylinder I18 is connected for operation, the shutoff valves 235 are closed to prevent oil from fiowing to the integral cylinders SI, 52, and the plugs 232 areinstalled in the hose connecting openings 23I, therefore there is no flow of oil downwardly through the main valve passage I45 when the valve member I48 is raised, hence when the valve I48 is raised to close off the exhaust opening I48, the oil flows around the valve piston I58, through the duct 288 and transversely across the vertical valve passage I81 around the valve neck 283 into the auxiliary casing 245 through the aligned openings 258, 258. This movement of the oil is interrupted by lowering the valve member I48 to uncover the exhaust opening I46, thereby relieving the pressure, whereupon the spring 254 closes the valve member 252. Attention is called to the fact that to move the piston 281 in the opposite direction, the same valve member I48 is not manipulated downwardly from the neutral position as in the operation of the integral cylinders, but

. a rather the valve member I43 of the valve mechanism I on the other side of the casing I20 is raised to create pressure in the supply duct associated therewith, whereupon oil under pressure is directed into the lower end of the auxiliary valve passage 243 on the right side of the casing 243 as explained above. Thus, itfis evident that the double acting cylinder piston 231 is moved in one direction by raising oneof the valve members I and in the other direction by moving the other valve member I48 on the other side of the valve casing I20. However, in the event that one .of thevalve members I40 is held in raised position until the piston 291 hits the end of the cylinder I10, the pressure rises in the supply duct I40, forcing the valve I01 open against the spring double acting piston 291 in the same direction;

The control mechanism for actuating the valve members I43 will now be described. Each of the valve heads 2|! is pivotally connected by means of a pin 30! to an actuating arm 303 fixed to a split hub 301 which is secured by a clamping bolt 303 to a tubular shaft 300 journaled in one of the side walls of the valve casing I20. The two tubular shafts 303 are disposed coaxiallyin laterally spaced arrangement with their inner ends spaced apart and their outer ends extending outwardly beyond the side walls of the casing I20, each of the outer ends carrying a hub 3I0 rigidly fixed thereto, on which is mounted an actuating lever 3. The tubular shafts 309 are held in alignment by a pair of central control shafts 3I2, which are joumaled in the tubular shafts 300 and have their inner ends journaled in a bearing lug 3I3 cast integrally with the casing I20, (see Figure 6). The inner ends of the central shafts 3I2 are supported in the bearing 3I3 in closely spaced relation, but are not interconnected and therefore the two shafts 3I2 are free to turn independently of each other. Thus, moving either of the levers 3II forwardly, rocks the tubular shaft 309 associated therewith in a counterclockwise direction as viewed in Figure 8, swinging the arm 306 upwardly and raising the associated valve member I48 in its passage I 45,-

-thereby,creating a pressure in the associated supply duct I40. Thevalve member I48 is returned to a neutral position by returning the control lever 3 to a vertical position, as illustrated in Figure 5. Similarly, by swinging the control lever 3II rearwardly, the tubular shaft 303 is rocked in a clockwise direction as viewed in Figure 8, thereby swinging the arm 306 downwardly and shifting the valve member I48 downwardly in the valve passage I to open the check valves I53, I04 and reset the exhaust valve I93, as explained hereinabove.

The control lever 3II is yieldably retained in adjusted position by means of a detent roller 3|! mounted on a stub shaft 3| which is journaled in a pair of lugs 3", the latter being formed integrally with an arm 3I0 carried on a hub 3|! which is iournaled on a shaft 320. The shaft 320 extends between the two side walls of I the casing and is supported therein, the center Jll of the shaft 320 being supported in an apertured lug 32I cast integrally with the casing I20. Each of the arms 3I3 extends rearwardly from the shaft 320 and bears upon a compression spring 322 which reacts upon a horizontal surface 323 (see Figure 9), within the casing I20. Thus, the pressure of the springs 322 force the-arms 3I3 upwardly to urge the detent rollers 3" into engagement with a pair of sectors 324, which are formed integrally with the hubs 331 and curved inwardly toward each other as indicated in Figure 6 into register with the rollers Ill. The edge of the sectors 324 are provided with centrally disposed notches 325 to receive the rollers II! when the control levers 3I I are in vertical or neutral position to retain them in that position, but when the levers 3I I are swung either forwardly or rearwardly from neutral position the rollers 3|! are forced downwardly about the axis of the supporting shaft 320, against the pressure of the springs 322, and as the tubular shafts are rocked in either direction, the rollers roll along the edge of the sectors and into engagement with one or another of a pair of notches 323 on opposite sides of the central notch 323. The notches 32! engage the rollers 3I5 to yieldably hold the control levers 3 in forward or rearward position.

Each of the central control shafts 3I2 is provided with an actuating arm 330 which is formed integrally with a hub 33I rigidly fixed to the respective shaft 3I2. Each of the arms 330 is connected by a swingable link 332 with a lug 333 formed integrally with the associated rockshaft arm 40 or H. Eachof the links 332 comprises a rod, the two ends of which are turned at right angles thereto and inserted through suitable apertures in the arm 330 and the lug 333, respectively. Thus it is evident that when either of the rockshafts 3I rocks, it acts through the associated link 332 to rock the associated control shaft 312 therewith. The outer end of each control shaft 3I2 extends beyond the adjacent hub 3| 0 of the control lever 3H and carries a hub 335 on which is integrally formed a cam 330. Each of the cams 336 is positioned toengage a tubular sleeve 331, the interior of which is threaded as indicated at 338 (Figure 6) for adjustably receiving the control lever 3| I. The cam 336 has a camming surface 339 (see Figure 5), which is generally helical in shape, increasing in radial dimension in a counterclockwise direction. The camming surface330 is adapted to engage the lower end of the sleeve 331 to return the control lever 3 t neutral position at various points in the range of movement of integral piston associated therewith. The upper ends of the sleeves 331 are provided with control handles 340 which are grapsed by the operator when he swings the control levers to actuate the hydraulic mechanisms and also to rotate the sleeves 331 on the threads 330 to adjust the lower ends of the sleeves 331 relative to the cam surfaces 330.

It is evident that when the handles 340 are moved forwardly to swing the sleeves 331 and control levers 3II forwardly in a clockwise direction as viewed in Figure 5, the pistons 43, 43 are caused to move rearwardly within the cylinders, swinging the rockshafts 3| in a clockwise direction and pushing rearwardly through the links 332 to swing the control shaft 3I2 and its associated cam 336 in a counterclockwise direction. Then, when it is desired to lower the load by rocking the rockshaf ts in a counterclockwise direction, the handles 340 are shifted rearwardly, eflecting terference with the sleeves.

ends ofthe sleeves 331, continued movement of the cams carrying the levers back to a vertical neutral position to stop the movement of the pistons. By screwing the sleeves 331 inwardly or outwardly on the levers ular movement of the cams 333 and hence the amount of angular movement of the rockshafts can be adjustably determined so that the load will always be lowered to a determined point.

In Figure 5, the sleeve 331 is shown in its upper extremity of movement corresponding to a-movement of'the associated piston 49 to the forward end of the cylinder 52. However, with the piston at the other end of the cylinder, the cam 336 is swung in a counterclockwise direction away from the sleeve 331. and the latter can be screwed downwardly on the lever 3 into a position in which the cam surface 339 engages the end of the sleeve at any desired position of the piston in the intermediate portion of the cylinder. This principle is especially useful in controlling cultivators, the depth of operation of which can be accurately adjusted by turning the sleeve 331, .after which the cultivators can be raised at the end of each crop row by swinging the handles 330 forwardly and then lowered at the beginning of the next row by swinging the handles'rearwardly, whereupon the cam 336 returns the control lever 3 to neutral, stopping the lowering action of the cultivators at exactly the predetermined position without further attention from the operator.

This. principle of preselecting the lowered position of the rockshaft is also set forth in the Worthington Patent -No. 2,403,422, mentioned hereinbefore, and is also described in detail in Patent No. 2,311,516 granted to Brown and Court, February 16, 1943.

It isbelieved that the operation of the hydraulic mechanism has been clearly explained above in connection with the various parts of the system and therefore a repetition of the explanation is not. considered necessary. It might be well to point. out, however, that Figures 5 and 8 show the mechanism prepared for operation of the integral cylinders 5|, 32, since the plugs 232 and 215 are shown installed in place of the hose connections 23, 21l to the single acting remote cylinders and the double acting cylinder 110. Figures '1 and 9 show the mechanism prepared for operation of the two single acting remote cylinders by showing the connecting hoses 234, while the valves 235 are shown closed and the plugs 215 are shown installed. Figures 3 and 11 show the mechanism prepared for operation of the double acting cylinder I10, with the hoses I'll, I12 connected tothe 3| I, the amount of an a 18 the exact details disclosed herein except as set forth in the following claims.

We claim:

1. Power lift mechanism for tractors and the like having an axle housing provided withan opening at one side and a pair of axle drive gears in said housing spaced apart in front of said opening to provide a limited space, said power lift mechanism comprising a casing adapted to be atauxiliary valve casing 245 and the plugs 232 in- I stalled; In this arrangement the shut-off valves 235 are closed also. Y

It isnecessary when preparing for operation of any remote cylinders to adjust the sleeve 331 outwardly on the control levers 3 far enough to insure that the cams 336 do not interfere with movements of the levers. This can also be taken care of by filling the integral cylinders 5|, 52 before closing the shut-off valves 235, This moves the cams 336 rearwardly far enough to avoid in- The cams are, of course, locked in position when the valves 235 are closed. 4

We do not intend our invention be limited to like having an axle 1 in overlapping relation rockshaft,

'spectively,

' nected to the piston vlike having a transverse tached to said housing over saidopening to form a closure therefor, a pair of lifting rockshafts :lournaled in said casing outside said axle housing with power receiving ends disposed in proximity to each other, a pair of motor units fixedly mounted on said casing andarranged in overlapping relation to each other to extend inwardly through the opening in said housing and into the limited space between said drive gears, one of said motor units being closer to its respective rock-' shaft than the other motor unit to the other rockshaft, and a. pair of actuating arms of unequal length fixed to said adjacent ends and extending radially in side by side relation and connected with said motors, respectively, the shorter of said arms being connected to said closer motor, the latter having a shorter stroke but having a capacity for exerting greater force upon its associated arm, whereby, the effects of the two motors on their respective rockshafts are substantially equal. 2. Power lift'mechanism for tractors and the housing provided with an opening at one side and a pair of axle drive gears in said housing spaced apart in front of said opening to provide a limited space, said power lift mechanism comprising a casing adapted to be attached to saidhousing over said opening to form a closure therefor, a pair of liftingvrock shafts journaled in said casing outside said axle housing with power receiving ends disposed in proximity to each other, a pair ders fixedly mounted on said casing and arranged to each other to extend inwardly through the opening in said housing and into the limited space between said drive gears, one of said cylinders being closer to its respective" rockshaft than the other cylinder to the other pistons slidable in said cylinders, reand a pair of actuating arms of unequal length fixed to said adjacent ends and extending radially in side by side relation and connected with the shorter of said arms being conin said closer cylinder, the stroke than the other piston and cylinder but havinga diameter sufllciently greater that the torque applied to the two rock hafts is substantially equal.

3. Power lift mechanism for tractors and the axle housing with an opening at one side and a pair of axle drive gears insa d housing spaced apart laterally in front of said opening to provide a limited space therebetween, said power lift mechanism comprising a casing adapted to be attached to said housing over said opening to form a closure therefor, a pair of liftin rockshafts journaled in said casing outside. said axle housing and disposed coaxially end to end, a pair of hydraulic cylinders with pistons therein, fixedly mounted on said casing and extending inwardly through said pistons,

latter having a shorter the opening in'said housing, one overlapping of unequal length fixed to said abutting ends and extending downwardly therefrom, the shorter of of hydraulic cylinprovided a eter than said upper cylinder whereby the torque applied to said rockshatts is substantially equal.

4. The combination set forth .in claim 3 including the further provision of supply ducts for said' cylinders, the duct for the cylinder of larger diameter being disposed beneath the latter and alongside said cylinder of smaller diameterr 1 r 5. In power 1m mechanism, a pair of m rockshaits dispom coaxially end to end, a pain of hydraulic cylinders withpis'tons therein disposed in juxtaposition in a compact arrangement near the adjacent ends of said rockshafts with one cylinder in overlapping relation to the other cylinder between the latter and said rockshafts, and a pair of actuating arms of unequal length the external diameter of the of larger diameter.

7. In a hydraulic power apparatus, a pair of rockshaftsdisposed coaxially with power receivfi'xed to the adjacent ends of said rockshafts, re-

spectively, and extending side by side radially from said rockshafts and connected with the two pistons, the shorter of said arms being connected with the piston in said one cylinder, the latter having a shorter stroke but greater. diameter than said other piston and cylinder toapply substantially equal torque at the two rockshafts.

6. In hydraulic power mechanism, a pair of rockshafts disposed coaxially with power recelving ends disposed in proximity to each other,

a pair of hydraulic cylinders disposed side by.

side in generally parallel arrangement near the adjacent ends of said rockshafts, with one cylinder disposed between the other cylinder and said rockshafts, a pair of actuating arms of unequal lengths fixed to the adjacent ends of said rockshafts, pistons in said cylinders-connected with said arms, respectively, the shorter of said arms being connected with the piston in said one cylinder, the latter having a shorter stroke but greater diameter than said other piston and cylinder to apply substantially equal torque at the two rockshafts, and supply ducts for said cylinders, the duct for the cylinder of larger diameter being disposed alongside said cylinder of smaller diameter in a compact arrangement in which the smaller cylinder and supply duct 00'- cupy a space of substantially the same width as in; ends disposed in proximity to each other, and

fiuid power mechanism for rocking said rockshafts, said mechanism being compactly arranged within a space limited by the distance.

between two planes spaced axially relative to said rockshafts, said mechanism comprising a first cylinder of comparatively large diameter and short length adjacent said power receiving ends of the rockshafts between said planes and extending generally parallel thereto, a second cylinder. of comparatively small diameter but longer length disposed along the side of said first cylinder remote from said rockshaits and slightly offset from said first cylinder in a direction parallel to the axis of said rockshafts, a fluid supply .duct for said first cylinder disposed along said remote side thereof and alongside said second cylinder, the latter and said duct having an overall dimension not greater than the distance between said spaced planes, 9. pair of comparatively short and long actuating arms fixed to said rockshafts, respectively, and extending to the ends of said cylinders, respectively, and pistons in said cylinders connected with said arms, respectively.

WAYNE HLWORTHINGTON. EMIL F. JIRBA.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Name Date 593,505 Gale Feb. 3,1393 2,009,137 Kleckner July 23, 1935 2,072,111 Keeler Mar. 2, 1937 2,107,760 McCormick Feb.'8, 1933 2,187,036 Kerber Jan. 16, 1940 2,221,462 Trambly Nov. 12, 1940 2,261,537 Moore Nov. 4, 1941 2,236,330 Traut June 16, 1042 2,303,727 Temple Jan. 19, 1943 2,337,633 Brown Dec. 23, 1943 

